Yarn twisting and winding machine



1957 w. s. HARRISON 3,334,828

YARN TWISTING AND WINDING MACHINE Filed May 22, 1964 4 Sheets-Sheet l PICK CYCL/E' P/CK CYCLE TRA VERSE CYCLE Wag 454m A ltorneys Aug. 8, 1967 w. s. HARRISON 3,334,823

YARN TWISTING AND WINDING MACHINE Filed May 22, 1964 4 Sheets-Sheet 2 I n 0 en to r Waz/amd/imefiafh/ee/sm/ Attorneys g- 1967 w. s. HARRISON 3,334,828

YARN TWISTING AND WINDING MACHINE Filed May 22, 1964 4 Sheets-Sheet 3 I nuenlor Ma /v 15/24/0127 15 452.50

wild mw A Horneys Aug. 8, 1967 Filed May 22, 1964 w. s. HARRISQN 3,334,828

YARN TWISTING AND WINDING MACHINE 4 Sheets-Sheet 4 A tlorney United States Patent 3,334,828 YARN TWISTING AND WINDING MACHINE William Siegfried Harrison, Abergavenny, England, as-

signor to British Nylon Spinners Limited, Pontypool, England Filed May' 22, 1964, Ser. No. 369,502 Claims priority, application Great Britain, May 25, 1963, 20,969/63 3 Claims. (Cl. 24226.1)

This invention relates to yarn winding machines arranged to produce tapered yarn packages of the so-called multicycle build and composite pirn build, the machine comprising a traverse mechanism arranged to reciprocate a yarn guide for a predetermined distance axially along a spindle on which a yarn package is to be wound, and traverse reversal control mechanism (hereinafter called the pick mechanism), which selects the traverse reversal points throughout the winding operation,

the traverse mechanism and the pick mechanism being driven by separate means.

The pick mechanism superimposes, in known manner, a reciprocating motion on the traversing motion, the pick frequency being substantially greater than one-half per unit package winding period, but being substantially less than the traverse frequency. For a multicycle package, the pick mechanism is in two parts superimposing a pick motion at each end of the reciprocating traverse motion, and thus it is possible to have a different pick frequency associated with each end of the package. For a composite pirn package, the pick mechanism forms only one end of the tapered package (usually the upper end), the other end being formed by a device which superimposes amotion on the traverse motion which causes the traverse reversal points at that end of the package to move gradually in one direction only.

It will be appreciated that a number of traverse cycles occur in each pick cycle. For convenience, the term pick cycle will be used to refer to the pick motion at either end of a multicycle package i.e. choosing one pick frequency to be representative of the two frequencies, if a different frequency is associated with each end of the package.

Ridging occurs when it is impossible to provide for a constant predetermined relationship between the traverse speed and the pick frequency when the traverse and pick mechanisms are separately driven since the speed with known forms of driving means may vary uncontrollably by as much as half percent. It has been found, for example, that ridging may occur when there is an unintentional quarter percent change in the traverse speed when the traverse mechanism is driven independently of the pick mechanism.

Such ridging is caused by the extremities of layers of ,yarn being laid upon the extremities of previously laid layers of yarn, as a result of reversals in corresponding traverse strokes in different (and possibly consecutive) pick cycles coinciding, Whereas the arrangement should be such that a substantial number of traverse reversal points do not occur at the same position on the yarn package.

The occurrence of ridges on the yarn package, apart from detracting from the appearance of the package, is undesirable if, for example, the yarn is to be used in hosiery, or in warp knitting when it is required that the yarn should be removed from the package at a constant low take-off tension, Whereas the presence of ridges leads to sudden variations in the take-0E tension occurring.

It is an object of the present invention to provide a yarn winding machine which will produce yarn packages without such ridges or Which will substantially reduce the tendency for ridges to be produced in these yarn packages.

According to the present invention, a winding machine in which the drive means for the pick mechanism is separate from the drive means for the traverse mechanism, has adjusting means for continuously cyclically varying the traverse speed, preferably at a frequency out of phase with the pick frequency.

The invention may be carried into practice in various ways but one embodiment and modifications thereof will now be described by way of example with reference to the accompanying drawings, in which:

FIGURE 1 shows diagrammatically the construction of a multicycle package,

FIGURE 2 shows diagrammatically the construction of a composite pirn package,

FIGURE 3 illustrates the traverse mechanism and pick mechanism of a winding machine having a ring-rail device of conventional fOITIl, the traverse mechanism being driven by hydraulic apparatus independently of the main drive means of the winding machine,

FIGURE 4 is a cross-section of a flow-regulating device for hydraulic drive means of FIGURE 3, the device causing the output of the drive means to vary continuously in a cyclic manner, and

FIGURE 5 is a front elevation of the device of FIG- URE 4.

A winding machine which is adapted to produce multicycle or composite pirn packages includes some form of pick mechanism in order to select the traverse reversal points during the winding operation.

Conveniently the pick mechanism comprises two cams in the case of a multicycle package, one controlling the upper traverse reversal point and the other the lower traverse reversal point. In the case of a composite pirn package the pick mechanism comprises one cam, a second cam being provided for controlling the lower traverse reversal points but not comprising part of the pick mechanism as hereinbefore defind, but is arranged to rotate at a slower speed than the cam of the pick mechanism. When a multicycle package is to be built the cams may be coupled so as to rotate together.

Thus a multicycle package will have a pick cyclic motion superimposed at both ends, as is seen in FIGURE 1, while a composite pirn package has a pick cyclic motion superimposed at one end only, (usually the upper end), as is seen in FIGURE 2;

If only one power source is provided in the winding machine for the spindle, traverse mechanism and pick mechanism, then it is possible to arrange that the traverse reversal points do not occur at the same position on the yarn package in different pick cycles.

However, if a source or sources of power additional to the main drive for the spindle are introduced into the machine, and the traverse mechanism is driven separately from the pick mechanism, then the inevitable tendency for the speed of these drives to drift implies that ridgeforming conditions are liable to occur during the winding operation.

This is because, unintentionally, the extremities of corresponding layers of yarn in different pick cycles occur at the same position on the yarn package, and consequently these extremities form a ridge. The change in the speed of the drive means may be as small as one-quarter percent but a drift of one-half percent is usual with known forms of drive means (particularly if it is electrical or hydraulic in form).

In one arrangement, shown in FIGURE 3, for produc ing a yarn package 1 of either a multicycle build or a composite pirn build, the yarn guide of a winding machine comprises a conventional ring device 2 moved axially along a vertically mounted spindle 3 on which the pack- 3 age 1 is being wound, the spindle 3 being driven by an electric motor (not shown).

The traverse mechanism of the winding machine includes a striker plate 5 rigidly secured to rod 50 which is rigidly secured to the ring rail 2a and is arranged to move in the same vertical plane as two vertically spaced limit switches 6 and 7, the positions of the switches being controlled by heart cams 3 and 9. The distance between the switches determines the traverse stroke length of the ring rail, reversals in the direction of movement of the ring rail 2a being caused by the plate 5 striking one or other of the switches. The pick motion is obtained by rotation of the cams 8 or 9 or both so as to alter the positions of the reversals.

The traverse mechanism also comprises a hydraulic ram 10 which is operated by the hydraulic pump 4. The flow of pressure fluid to the ram is reversed by a valve 11, displacement of switch 6 or 7 by the striker plate 5 causing the energisation of one of two solenoids 12 which operate the valve 11 to reverse the fluid flow through the valve. The operation of the hydraulic apparatus is conventional in form, pressure fluid being drawn from a reservoir 13 by the pump- 4, and into which reservoir it is exhausted from the ram, via the valve 11. An electrical supply 14 is provided so as to be capable of energising each of the solenoids 12.

When a simple multicycle build yarn package is being built (as shown diagrammatically in FIGURE 1), the cam 9 is mounted on the same shaft 16, driven by suitable means, as cam 8, in such manner that the lower limit switch 7 moves at a fixed distance from the other limit switch 6. However, when a composite pirn build is required (as shown diagrammatically in FIGURE 2), the cam 9 is driven by any convenient separate means, such that it performs a half-revolution during the period the yarn package is being wound, the lower limit switch 7 being raised through half a stroke in this period.

Conveniently, the driving means for either cam 8 or 9 is associated with the spindle drive means or comprises independent means.

The traverse drive means of FIGURE 3 is cyclically varied by incorporation of valve mechanism in the hydraulic drive means, which valve mechanism comprises a flow-control device 22 as shown in greater detail in FIGURES 4 and 5. Pressure fluid in the exhaust pipe 23 returning from the ram 10 operating the traverse mechanism passes through a pressure-responsive valve 24 and then an adjustable metering orifice device 25 before passing to a reservoir, not shown in FIG. 4.

The valve 24 comprises a piston member 26 having an enlarged diameter head 27 at one end. The end surface 28 of the head 27 is in communication with a part 29 of the pipe 23 beyond the metering orifice device 25, while the surface 30 of the head is in communication with a part 31 of the pipe 23 between the valve 24 and the metering orifice device 25. The smaller-diameter part 32 of the piston member 26 has a landed part 33 arranged to be capable of preventing the flow of pressure fluid from the ram, but is resiliently biased towards its open position by a compression spring 34 acting on the head 27.

Y Thus the setting of the metering orifice device 25 controls the rate of flow of the pressure fluid, and hence the speed of operating of the ram. If the pressure difference across the metering orifice device is such that a pressure builds up in the part 31 of the pipe 23 due to the rate of fluid flow being too high, then the piston member 26 moves so as to tend to reduce the flow, and vice versa.

The metering orifice device 25 comprises a piston member 35 axially mounted in the part 29 of the pipe 23, the part 31 of the pipe 23 between the valve 24 and the orifice device 25 being in communication with the part 29 through a port 36. The piston 35 is so positioned that a change 'in the eifective size of the port 36 can be caused by an axial displacement of the piston 35.

Movement of the piston 35 is allowed by providing a screw-threaded end portion 37 on the piston which co- .operates with the end of the part 29 of the pipe 23, the piston position being manually adjustable by turning a knob 38 on the screw-threaded portion 37. An O-ring seal 39 prevents leakage of pressure fluid to the screwthreaded portion 37.

In order to reduce the tendency for ridge-forming conditions to occur, the position of the piston member 35 isvaried continuously in a cyclic manner by separate adjusting means, such that the rate of fluid flow and hence the rate of operation ofthe traverse mechanism is varied by approximately 17%.

As can be seen more clearly in FIGURE 5, the said separate adjusting means comprises a mechanical linkage 40 arranged between the knob 38 and a cam 41, the shape of the groove 41a of the cam 41 being such that the mechanical linkage 40 which is constrained to follow the groove of cam 41 causes the knob 38 to oscillate about its pre-set position. As illustrated, the groove of cam 41 is heart-shaped, although other shapes maytbe employed. If the knob 38 is required to be re-set ina new mean position, then it may be necessary to rearrange the linkage 40 so that the scrambling effect of the adjusting means remains substantially the same. The drive means for this cam 41 may be any convenient source of power, and may comprise an individual source or a take-off from any suitable power source of the machine. It will be appreciated, that it is immaterial whether the drive means for this cam is subject to drift or not.

What I claim is:

1. In a yarn winding machine of the type suitable for winding multicycle and composite pirn packages, said machine having a rotatable spindle on which a yarn support may be mounted for winding a yarn package thereon, a traverse mechanism including a yarn guide reciprocable in a plane parallel to the axis of said spindle, drive means for reciprocating said yarn guide along a stroke path between reversal points, a pick mechanism for cyclically varying the point at which said stroke path ends in a manner to produce a yarn package having at least one tapered end, and separate drive means for said pick means, the improvement which comprises means for reducing the ridging of yarn at a tapered end of a package being wound on said support, said means including adjusting means associated with said yarn guide drive means for cyclically varying the traverse speed of said yarn guide whereby a substantial number of traverse points do not occur at the same position on the yarn package.

2. A yarn winding machine as in claim 1 in which said 'drive means for said pick mechanism imposes pick cyclic motion at both ends of the traverse motion at a frequency less than the traverse frequency whereby a yarn package having two tapered ends is formed.

3. A yarn winding machine as in claim 1 wherein said adjusting means is constructed and arranged to vary the traverse speed by approximately i-7% and at a frequency out of phase with the pick frequency.

References Cited UNITED STATES PATENTS 2,529,559 11/1950 Kreamer.

2,575,031 11/1951 Smith 242-26.1 2,647,698 8/ 1953 Woolley 24226.1 2,749,055 6/1956 Bauer 242-26.2 2,764,363 9/ 1956 Stammwitz 24226.2 3,042,326 7/1962 Lamb et a1. 24226.3 3,130,930 4/ 1964 Miller 24226.3

FOREIGN PATENTS 626,177 7/ 1949 ,Great Britain.

STANLEY N. GILREATH, Primary Examiner. 

1. IN A YARN WINDING MACHINE OF THE TYPE SUITABLE FOR WINDING MULTICYCLE AND COMPOSITE PIRN PACKAGES, SAID MACHINE HAVING A ROTATABLE SPINDLE ON WHICH A YARN SUPPORT MAY BE MOUNTED FOR WINDING A YARN PACKAGE THEREON, A TRAVERSE MECHANISM INCLUDING A YARN GUIDE ALONG CIPROCABLE IN A PLANE TO THE AXIS OF SAID SPINDLE, DRIVE MEANS FOR RECIPROCATING SAID YARN GUIDE ALONG A STROKE PATH BETWEEN REVERSAL POINTS, A PICK MECHANISM FOR CYLICALLY VARYING THE POINT AT WHICH SAID STROKE PATH ENDS IN A MANNER TO PRODUCE A YARN PACKAGE HAVING AT LEAST ONE TAPERED END, AND SEPARATE DRIVE MEANS FOR SAID PICK MEANS, THE IMPROVEMENT WHICH COMPRISES MEANS FOR REDUCING THE RIDGING OF YARN AT A TAPERED END OF A PACKAGE BEING WOUND ON SAID SUPPORT, SAID MEANS INCLUDING ADJUSTING MEANS ASSOCIATED WITH SAID YARN GUIDE DRIVE MEANS FOR CYCLICALLY VARYING THE TRAVERSE SPEED OF SAID YARN GUIDE WHEREBY A SUBSTANTIAL NUMBER OF TRAVERSE POINTS DO NOT OCCUR AT THE SAME POSITION ON THE YARN PACKAGE. 